Rotary fluid pump mechanism and the like



v197.0 s. o. STAGEBERG 3,544,243

ROTARY FLUID PUMP MECHANISM AND THE LIKE Filed Sept. 10, 1968 2 Sheets-Sheet 1 INVENTOR.

STERLING o. STAGEBERG ATTORNEYS Dec. 1, 7 s. o. STAGEBERG 3,544,243

ROTARY FLUID PUMP MECHANISM AND THE LIKE Filed Sept; 10, 1968 2 Sheets-Sheet 2 I 1 2 4 22 E LL.

I 9 I Q g S I Q l & O ommwro o v $8898, a In 3 N g I Q Q N N Q m mm qr fiam 3 INVENTOR.

STERLING O. STAGEBERG BY ATTORNEYS United States Patent 3,544,243 ROTARY FLUID PUMP MECHANISM AND THE LIKE Sterling O. Stageberg, 985 Alt. 19, Rte. 1, Palm Harbor, Fla. 33563 Filed Sept. 10, 1968, Ser. No. 758,907 Int. Cl. F04c 1/00, 17/00 US. Cl. 418-58 6 Claims ABSTRACT OF THE DISCLOSURE A fluid pump comprises a driven rotor having a cylindrical wall which rotates about a hub structure eccentric therewith, and a plurality of flexible, deformable bandlike vanes attached at one end to the rotor and at the other end to the hub form flexing sides of pump chambers which expand and contract when the rotor is driven. A radial end plate at one end of the rotor and a fixed radial port plate adjacent the opposite end of the rotor are sealingly engaged by the side edges of the vanes and form rigid sides of the pump chambers. The ends of adjacent vanes are overlapped and clamped to the hub and rotor to form continuous fluid tight ends for the pump chambers. The portions of the vanes adjacent the hub are supported against destructive flexure by blocks which permit fluid to flow from between the vanes and their supports.

BACKGROUND OF THE INVENTION The present invention relates to rotary displacement devices, such as fluid pumps or motors and is an improvement on the type of rotary cylinder pump disclosed in applicants United States patent No. 2,444,234. The patented pump comprises a hollow cylindrical rotor having a closed radial end wall and which is adapted to be rotated about an axis eccentric to the axis of a hub within the rotor. Flexible band or ribbon-like vane members are attached at one end to the hub at spaced intervals and extend radially in spirals or loops outwardly in the direction of rotation of the rotor and the outer ends are attached at spaced intervals to the cylindrical wall of the rotor whereby the vanes form flexible side walls of outwardly curving pump chambers which expand and contract during each revolution of the rotor because of the eccentric movements of the opposite ends of the vanes. The other opposite sides of the pump chambers are formed by the radial wall of the rotor and a port plate disposed radially of the cylindrical walls of the rotor and the edges of the vanes engage these .sides to form a sliding seal. The port plate has elongated curved inlet and outlet openings which admit fluid to the pump chambers during their expanding movements and discharge fluid as the chambers move through their contracting movements. To prevent destructively sharp bending of the flexible vane members adjacent the hub backing blocks have curved vane supporting surfaces about which portions of the vanes wrap and unwrap during operation of the pump.

In the patented construction, it is diflicult to prevent leakage of fluids from between the rotor and the port plate and between the hub and the radial wall of the rotor and the port plate. Also, fluid becomes trapped between the vanes and their respective backing surfaces during the interval the pump chambers travel between the discharge and inlet ports and this trapped liquid causes the hub to tend to rotate faster than the rotor. The patented construction utilized a torsion spring to accommodate such temporary overrunning and is effective when compressible fluids are pumped but which present problems when non-compressible fluids are pumped.

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THE PRESENT INVENTION A principal object of the present invention is the provision of a new and improved pump of the character referred to which is particularly effective in pumping liquids and which may be operated dry for indefinite periods at relatively high r.p.m.s without adversely affecting its pumping characteristics, which initiates pumping operations without priming, and is not adversely affected by grit, dirt and foreign particles in liquids pumped thereby.

Another object of the invention is to provide a new and improved pump of the character mentioned in which surfaces of the rotor and hub structure have no fluid sealing functions so that the rotor is preferably spaced from the port plate and the hub structure is preferably spaced from the rotor and the port plate thereby eliminating maintenance of close tolerances in the manufacture of the pump.

It is another object of the present invention to provide an improved pump of the general type described in which the vane members are joined together at their ends and attached to the rotor and hub so that the ends of the pump chambers are formed by contiguous joining of the vanes forming opposite sides of the pump chambers whereby the only fluid seals between relative moving parts which are subjected to fluid passing through the pump are formed by edges of the vanes engaging smooth wall surfaces.

A further object of the invention is the provision of an improved pump of the character described in which fluid cannot become trapped between the vanes and their backing surfaces thereby eliminating tendency of the hub to overrun the rotor.

A more specific object of the invention is the provision of a pump of the character mentioned in which the vane members are attached to the hub and rotor structures by overlapping end portions of adjacent vanes and clamping the vanes to the structures whereby the edges of the vanes engaging the radial end wall and the port plate form fluid tight running seals therewith so that in the assembly of the pump the edges of the vanes may be compressed between the end rotor wall and port plates and provide exceedingly low friction, close running tolerances upon rotation of the rotor.

Other objects and advantages of the invention will be apparent from the following description of a preferred form thereof, reference being made to the accompanying drawings wherein:

FIG. 1 is a fragmentary end elevational view of a water pump embodying the invention;

FIG. 2 is a sectional view of the pump similar to FIG. 1 taken on line 22 of FIG. 3; and

FIG. 3 is a sectional view taken along line 33 of FIG. 2.

While I have described my invention as a pump, it is to be understood that the invention may be embodied in any type of device having expansible chambers, such as a pump, compressor, motor or similar structure and that the word pump, when used in the specification and claims should be so interpreted.

Referring to the drawings, my invention is shown embodied in a water pump 10 which comprises a housing 11 formed by a generally drum shaped member 12 having an end assembly 13 secured across an open end by bolts secured to a flange about the periphery of the member. A pump drive shaft 15 is journaled by bearings 16 in a sleeve 17 formed on the member 12 and extending axially thereof. An oil seal 18 retains lubricant in the sleeve. The end assembly 13 includes a port plate 20 having tubular coupling members 21, 22 formed thereon and a wear plate 23. The port plate 18 may be conveniently formed of a suitable plastic and the couplings 21, 22 provide means to connect the intake and discharge of the pump to suitable hoses or the like. The wear plate 23 is preferably of stainless steel and forms the inner surface of the end assembly. The housing 11 may also include means to attach the pump to a support and in driving relation to a motor or engine connected to the shaft 15. For the sake of brevity such means and motor are not shown. The shaft 15 rotates a pump assembly counterclockwise, as viewed in FIG. 2, inside the housing member "12 which draws water into the intake member 21 and discharges the water through the discharge member 22. The pump assembly comprises a cup shaped rotor 24 having a cylindrical wall 25 and a fluid impervious radial- 1y extending end wall 26. A socket 27 is formed integral with the end wall 26 and the inner end of the drive shaft 15 is suitably secured to the walls of the socket so that the rotor 24 is rotated by the shaft about an axis coincident with the axis of the cylindrical wall 25. The edges of the open end of the cylindrical wall 25 are preferably spaced an appreciable distance from the wear plate 23, and the journalling of shaft 15 is such as to prevent endwise movements of the shaft and shifting of the rotor toward and from the wear plate.

A hub structure 30is journaled for free rotation about a stub shaft 31, one end of which is secured in a socket 32 in the end assembly 13, and the axis of which shaft is parallel and eccentric to the axis of rotation of the rotor 24. The hub structure includes an octagonal member 33 having an axial socket 34 which receives the stub shaft 31. Prefera-bly,a needle bearing 35 is interposed between the shaft and walls of the socket 34. It will be noted that the length of the hub member 33 is such that an appreciable clearance exists between the ends thereof and the plate 23, and the wall 26 of the rotor.

Eight identical vane members having reference characters 36 to 43 have one end attached to the hub structure 30 andthe opposite end attached to the rotor wall 25. The vane members are formed of bands or ribbons of suitable fluid impervious, flexible and slightly deformable material such as a suitable fabric, leather, flexible metals, or any of the rubber substitutes or so-called plastics now well known in the art and which have the characteristics desired. The vanes 36-43 are disposed with the transverse sections thereof extending parallel to the axes of the rotor 24 and the hub structure 33 so that the edges thereof sweep the opposed surfaces of the plate 23 and rotor wall 26. The width of the vanes36-43 prior to assembly in the pump is slightly in excess of the distance between the inside surface of the plate 23 and the inside face of the end wall 26 so that when the rotor 24 is assembled in the housing 12, the opposite side edges of the vanes will be slightly deformed by compression and will closely engage the surfaces of the plate and wall. Upon initial operation of the pump, the edge portions of the vanes quickly form a low friction, fluid tight running seal with the surfaces engaged thereby. Preferably, the surfaces of the plate 23 and end wall 26 engaged by the edges of the vanes are polished to enhance the sealing qualities of thepump assembly.

The .vane members 36-43 are substantially longer than the maximum distance between the hub structure 30 and the rotor wall 25 and curve or loop from the hub structure outwardly in the direction of rotation of the rotor. It will be seen that adjacent vane members 36-43form opposite flexible sides ,of a pump chamber, the other sides of which are formed by the plate 23 and the end wall 26. When the rotor 24 is driven by the shaft 15 torque is applied to the hub structure 30 through the vanes 36-43 and the pump assembly rotates, causing expansion in vol ume of the pump chambers as they swing through 180 from the bottom to the top of the pump, as viewed in FIGS. 1, 2, and contraction in volume as they swing from top to bottom of the pump.

The port plate 18 and the plate 23 of the end assembly portion of vane 36, for example, overlaps a substantial end 13 have aligned arcuate openings or ports 44, 45 therein which are positioned and arranged so that the'port 44 is open to the sides of the pump chambers during a substantial portion of their expansion movement for the intake of fluid. The port 45 is open to the sides of the pump chambers during their contracting movement so that fluid is expelled from the chambers through the port. The ends of the ports 44, 45 are angularly spaced apart so that as the pump chambers swing from their expanding cycles to their collapsing cycles and vice versa during each of their revolutions they are closed to both of the ports. The plate 18 is formed to provide a passage between the inlet connection 21 and port 44 and between the port 45 and the outlet connection 22.

Animportant feature of the invention is the manner in which the vane members 36-43 are attached to the hub structure 30 and the rotor wall 25. Referring to the hub structure 30, the inner end portions of each two adjacent vane members are secured to one of the octagonal faces of the member 33 in overlapping contiguous relation and clamped thereto. The flexible, deformable character of the material forming the vanes causes these overlapping and compressed portions to form continuous fluid tight end structures for the fluid chambers.

As a specific example of effecting the seals described, referring to the vane 36, the inner end section of the vane is clamped to two adjacent octagonal faces of the hub 33 and overlies the end portion of the vane 43. In turn, the end portion of vane 36 is overlapped by the end portion of the vane 37, as shown. As may be seen, each of the vanes overlaps an adjacent vane in the manner described. Vane 36 is engaged by a metal clamp member 50 which has a flat surface 51 resting on the vane and a convexly curved side surface 52 about which the vane may wrap as the pump assembly rotates. The block 50 is attached to the hub member 33 by a bolt 53 and is retained in alignment with the adjacent octagonal face of the hub member by dowels 54. The overlapping vanes on each octagonal face of the hub member 33 are clamped to the hub memher by clamp blocks like the block 50 and to avoid repet1 tion these blocks are not described in detail and are referred to by the same reference character.

The surfaces 52 of the blocks 50 provide support surfaces for the vanes and prevent sever and damaging flexure of the vanes. To maintain a desirable configuration of the pump chambers the sides 54 of the clamp members 50 are convexly curved to provide back-up supports for the vanes on the sides opposite thev sides supported by the surfaces 52.

It is to be noted that the length of the blocks 50 is the same as that of the hub member 33 which provides flow spaces 55 between the ends thereof and the adjacent plate 23 and end wall 26. These flow spaces permit fluid to pass from between the respective vanes and the adjacent side 52 of the clamping block for the vanes to the space between the next vane and the surface 54 of 'its clamping block. Thus, as the vane moves to the end of the compression stroke and out of alignment with the outlet port 45, the fluid of the contracting pump chamber may flow to the next pump chamber commencing to expand. In high speed pumps, it may be desirable to provide additional flow passages through the blocks 50 from the surface 52 to the surface 54 and this is accomplished by providing bores 56 from one side of the blocks to the other, as shown.

The outer ends of the vanes 36-43 are attached to the rotor wall 25 to form overlapping seal portions with adjacent vanes so that the outer ends of the pump chambers are effectively and efficiently closed by a construction similar to that of the inner ends.

Referring to FIG. 2, it will be seen that the outer end section of the vane 43 which lies against the wall 25, and the end section of vane 36 which lies against the wall 25 is overlapped by a portion of the next vane 37. The overlapping and overlapped portions of the vanes are clamped together and to the wall by curved clamp members 60 which are tapered at their ends and are secured to the wall by rivets 61.

It will be observed that during operation of the pump the only relative movements between the pump chamber forming elements are the edges of the vanes 36-43 and the solid portions of the plate 23 and the end wall 26. This movement occurs as the vanes flex during their expansion and contraction movements of the pump chambers and is relatively minor. The friction developed at these engaging surfaces is minimal and because of the physical characteristics of the vanes, these elements fit in close yet freely moving fluid containing relation.

It will be appreciated that the present invention provides an exceedingly efiicient fluid pump which can be manufactured with a minimum of attention to tolerances and with relatively slight machining. This arises from the fact that the end portions of adjacent vanes which form pump chambers are contiguous or join directly with one another to form sealed ends of the pump chambers and that the physical characteristics of the vanes cause the edge portions thereof to form fluid tight self-adjusting seals with the walls forming the opposite rigid sides of the pump chambers. It is obvious that liquids moved through the pump may contain a high degree of grit and foreign material which, due to the deformable resilient character of the vanes will accommodate such foreign particles without affecting the sealing qualities or causing detrimental abrasion of the pump parts. Because the rotor 24 and the hub structure engage no other relative moving surfaces these parts can be manufactured and assembled with a minimum of attention to close tolerances, etc. The fact that the pump is of symmetrical form and operation enables it to be operated at high speeds, such as 7,000 r.p.m. and above, so that a relatively small dimensional pump can move relatively large volumes of fluids. An outstanding feature of the pump is the fact that it may operate dry and without lubrication for extended periods because of the self-accommodating fits between the relatively moving parts of the vanes and the plate 23 and wall 26, and yet retain efliecient sealing to enable the pump to draw water a height of ten feet and more without priming.

Although I have described but one form of the invention it is understood that other forms, modifications and adaptations could be made all falling within the scope of the claims which follow.

I claim:

1. A pump structure including a pump chamber comprised of two band shaped flexible vane members generally co-extending in confronting spaced apart relation whereby said members form flexible opposed side walls of said pump chamber, means joining the adjacent end portions of said vane members together at opposite ends thereof to form an uninterrupted enclosure by the material comprising said members, means forming two spaced apart rigid wall surfaces engaging and extending normal to opposite edges of said vane members and forming two 0pposite sides to said pump chamber and providing a pump inlet and pump outlet, means for flexing said vane members to expand and contract the volume of said chamber, characterized by the last mentioned means comprising a hub structure between said wall surfaces and including a support surface thereon, one end section of one of said vane members lying against said support surface and an end section of the other of said vane members overlapping the first mentioned end section, the opposite edges of said vane members including said overlapping sections forming fluid seals with said rigid wall surface, and means securing said overlapping sections to one another and to said support surface.

2. A pump structure as defined in'claim 1 further characterized by said means for flexing said vane members comprising a rotor having a wall section surrounding said hub structure and between the planes of said wall surfaces the other end setcion of one of said vane members opposite said one end section thereof attached to said rotor wall section and the other end section of the other vane member opposite said one end section thereof overlapping the said other end section of the first mentioned vane member on said rotor wall section, the opposite edges of said overlapping vane sections forming fluid seals with said rigid wall surfaces, and means securing said overlapped sections together and to said rotor wall section.

3. A fluid pump and the like comprising a rotor having a wall and adapted to rotate in a given direction about and eccentric to the axis of a hub structure, a plurality of flexible band-like van members extending radially from said hub structure, said vane members attached at one end to said hub structure and attached at the other end to said rotor wall with the transverse sections of said vane members extending parallel to said axis, said vane members curving from said hub structure outwardly to said rotor, wall means forming two spaced apart rigid wall surfaces extending generally normal to the opposite edges of said vane members and engaged by said vane member edges to form a fluid seal for the area between said vane members and said rigid wall surfaces nad providing a pump inlet and a pump outlet, characterized by the outer end sections of said vane members engaging said rotor wall end sections of one vane member overlapping the outer end segment of one adjacent vane member to form fluid seals between the adjacent ends of said vane members and with said rigid wall surfaces.

4. A fluid pump and the like as defined in claim 3 further characterized by the end portions of adjacent vane members being disposed in overlapping positions at said hub structure, and clamp means forcing said overlapped portions to said hub structure and rotor wall respectively.

5. A fluid pump and the like as defined in claim 4 further characterized by means at said hub structure forming curved surfaces to support said vane members adjacent said hub during flexure of said vane members t0- wards a volume reducing movement of said chamber, and fluid passage means leading from said curved surfaces to facilitate escape of fluid from between said curved surfaces and the vane members moving thereagainst.

6. A fluid pump and the like as defined in claim 4 further characterized by said clamp means including a curved support surface adapted to be engaged by and to support one of said vane members as said vane member is flexed in a direction to constrict the volume of said pump chamber, said clamp means having a fluid passage from said curved surface to another surface thereof for permitting flow of fluid from between the last mentioned vane member and said curved supporting surface.

References Cited UNITED STATES PATENTS 1,086,488 2/1914 Wachter 1031 17 2,336,580 12/ 1943 Yeatrnan 103-121 2,444,234 6/1948 Stageberg 103121 2,882,830 4/1959 McDufiie 103-121 3,381,583 5/1968 Vansteen 9156 FOREIGN PATENTS 630,507 10/ 1927- France. 355,042 8/ 1931 Great Britain. 857,530 12/ 1960 Great Britain.

HENRY F. RADUAZO, Primary Examiner U.S. Cl. X.R. 

